CN114099033A - supporting structure - Google Patents
supporting structure Download PDFInfo
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- CN114099033A CN114099033A CN202010879992.5A CN202010879992A CN114099033A CN 114099033 A CN114099033 A CN 114099033A CN 202010879992 A CN202010879992 A CN 202010879992A CN 114099033 A CN114099033 A CN 114099033A
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- support structure
- elastic member
- shaft
- drive shaft
- reciprocating
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- 230000033001 locomotion Effects 0.000 claims description 148
- 238000004140 cleaning Methods 0.000 claims description 21
- 239000004033 plastic Substances 0.000 claims description 4
- 229920001169 thermoplastic Polymers 0.000 claims description 3
- 239000004416 thermosoftening plastic Substances 0.000 claims description 3
- 230000009471 action Effects 0.000 claims description 2
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000005452 bending Methods 0.000 description 51
- 230000000474 nursing effect Effects 0.000 description 10
- 238000006073 displacement reaction Methods 0.000 description 7
- 238000005381 potential energy Methods 0.000 description 6
- 230000004044 response Effects 0.000 description 5
- 238000011010 flushing procedure Methods 0.000 description 4
- 230000001788 irregular Effects 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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Classifications
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- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/16—Power-driven cleaning or polishing devices
- A61C17/22—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/02—Rinsing or air-blowing devices, e.g. using fluid jets or comprising liquid medication
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/16—Power-driven cleaning or polishing devices
- A61C17/22—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like
- A61C17/225—Handles or details thereof
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/16—Power-driven cleaning or polishing devices
- A61C17/22—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like
- A61C17/32—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating
- A61C17/34—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating driven by electric motor
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/16—Power-driven cleaning or polishing devices
- A61C17/22—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like
- A61C17/32—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating
- A61C17/34—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating driven by electric motor
- A61C17/3409—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating driven by electric motor characterized by the movement of the brush body
- A61C17/3418—Rotation around the axis of the toothbrush handle
-
- A—HUMAN NECESSITIES
- A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
- A61C—DENTISTRY; APPARATUS OR METHODS FOR ORAL OR DENTAL HYGIENE
- A61C17/00—Devices for cleaning, polishing, rinsing or drying teeth, teeth cavities or prostheses; Saliva removers; Dental appliances for receiving spittle
- A61C17/16—Power-driven cleaning or polishing devices
- A61C17/22—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like
- A61C17/32—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating
- A61C17/34—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating driven by electric motor
- A61C17/3409—Power-driven cleaning or polishing devices with brushes, cushions, cups, or the like reciprocating or oscillating driven by electric motor characterized by the movement of the brush body
- A61C17/3445—Translation along the axis of the toothbrush handle
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- Health & Medical Sciences (AREA)
- Public Health (AREA)
- Epidemiology (AREA)
- Life Sciences & Earth Sciences (AREA)
- Animal Behavior & Ethology (AREA)
- General Health & Medical Sciences (AREA)
- Dentistry (AREA)
- Veterinary Medicine (AREA)
- Transmission Devices (AREA)
- Brushes (AREA)
- Oral & Maxillofacial Surgery (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Motor Power Transmission Devices (AREA)
- Support Of The Bearing (AREA)
Abstract
本发明提供一种支撑结构，其支撑作往复运动的驱动轴，该支撑结构(20)包括支撑结构内固定圈(23)、至少一个支撑结构弹性件(22)以及支撑结构外固定圈(21、51)，支撑结构内固定圈(23)被紧固于驱动轴(10)上，支撑结构外固定圈(21)被紧固于装置下壳体的内壁上，支撑结构弹性件(22)分布于支撑结构的外固定圈(21)和内固定圈(23)之间，在支撑结构弹性件(22)的垂直于驱动轴(10)径向的横截面上沿垂直于驱动力(F1)方向的宽度(b1)大于该支撑结构弹性件(22)的垂直于驱动轴(10)径向的横截面上沿平行于驱动力(F1)方向的厚度(t1)的三倍。该支撑结构具有低噪音，低能量损耗，低成本，且结构简单，适于批量生产的优点。
The invention provides a support structure, which supports a reciprocating drive shaft, the support structure (20) comprising a support structure inner fixing ring (23), at least one support structure elastic member (22) and a support structure outer fixing ring (21) , 51), the inner fixing ring (23) of the supporting structure is fastened on the drive shaft (10), the outer fixing ring (21) of the supporting structure is fastened on the inner wall of the lower casing of the device, and the elastic member (22) of the supporting structure is fastened on the inner wall of the lower casing of the device. Distributed between the outer fixing ring (21) and the inner fixing ring (23) of the support structure, on the cross section of the elastic member (22) of the support structure perpendicular to the radial direction of the drive shaft (10) along a direction perpendicular to the driving force (F 1 ) The width (b 1 ) in the direction is greater than the thickness (t 1 ) along the direction parallel to the driving force (F 1 ) on the cross section of the elastic member (22) of the supporting structure which is perpendicular to the radial direction of the driving shaft ( 10 ). times. The supporting structure has the advantages of low noise, low energy loss, low cost, simple structure, and is suitable for mass production.
Description
Technical Field
The present invention relates to a support structure, and more particularly, to a support structure for supporting a driving shaft reciprocating in an electric cleaning and nursing tool.
Background
Typically, a drive shaft that undergoes reciprocating motion (e.g., reciprocating rotational motion or reciprocating linear motion) needs to be supported by one or more supports to maintain its proper operation. In the prior art, a shaft-hole matching structure such as a shaft sleeve is used for supporting the driving shaft, and the driving shaft and a shaft sleeve hole are in clearance fit, so that the supporting structure tends to have larger noise and energy loss. The drive shaft may also be supported by bearings, for example, a ball bearing for reciprocating rotational movement and a linear bearing for reciprocating linear movement, however, the cost of using a bearing support is high.
Disclosure of Invention
The object of the present invention is to provide a support structure for supporting a driving shaft for reciprocating motion, which has advantages of low noise, low energy consumption, low cost, and simple structure, and is suitable for mass production.
In order to achieve the above object, in the present invention, at least a portion of the driving shaft is located in a lower stationary device housing, the driving shaft reciprocates along/around its longitudinal axis relative to the lower device housing under the driving force, the lower stationary device housing further comprises a support structure for supporting the driving shaft, the upper stationary device housing further comprises a head driven by the driving shaft, a transverse axis of the head is substantially perpendicular to the longitudinal axis of the driving shaft, wherein the support structure comprises a support structure inner retainer ring, at least one support structure elastic member, and a support structure outer retainer ring, the support structure inner retainer ring is fastened to the driving shaft along a circumferential direction of the driving shaft, the support structure outer retainer ring is fastened directly or indirectly to an inner wall of the lower device housing, the support structure elastic member has a spring property, and is distributed between the support structure outer retainer ring and the support structure inner retainer ring, the outer end of the supporting structure elastic part is fixedly connected with the outer fixing ring of the supporting structure, the inner end of the supporting structure elastic part is fixedly connected with the inner fixing ring of the supporting structure, wherein the width which is perpendicular to the driving force direction is distributed on the cross section which is perpendicular to the radial direction of the driving shaft of the supporting structure elastic part, the thickness which is parallel to the driving force direction is distributed on the cross section which is perpendicular to the radial direction of the driving shaft of the supporting structure elastic part, and the width which is perpendicular to the driving force direction of the supporting structure elastic part is more than three times of the thickness which is parallel to the driving force direction.
The support structure outer retainer ring, the support structure spring and the support structure inner retainer ring may be made of plastic, preferably thermoplastic, and the support structure inner retainer ring and the drive shaft may be injection molded as a unitary piece. The support structure springs may also be integrally coupled with the inner and outer retainer rings of the support structure.
Preferably, the support structure elastic member is provided so that a length thereof in a radial direction of the drive shaft is more than three times a thickness thereof in a cross section perpendicular to the radial direction of the drive shaft in a direction parallel to the driving force direction.
In one embodiment, the support structure spring has a thickness of 0.1mm to 1.3mm in a cross section perpendicular to a radial direction of the drive shaft in a direction parallel to the driving force direction. In another embodiment, the support structure spring has a thickness of 0.2mm to 0.7mm in a cross section perpendicular to a radial direction of the drive shaft in a direction parallel to the driving force direction.
The electric cleaning and care implement of the present invention is preferably an electric toothbrush or a dental irrigator, and the support structure is a linear motion support structure for supporting a drive shaft which is linearly reciprocated along a longitudinal axis. Preferably, the distance between the upper surface of the inner and outer fixing rings of the linear motion support structure and the head is smaller than the distance between the upper edge of the elastic member of the linear motion support structure and the head, or the distance between the lower surface of the inner and outer fixing rings of the linear motion support structure and the head is larger than the distance between the lower edge of the elastic member of the linear motion support structure and the head, so that the combined linear motion support structure is in a concave shape on at least one of the upper and lower sides of a cross section parallel to the longitudinal axis of the driving shaft performing reciprocating linear motion. Preferably, the maximum amplitude of movement of the reciprocating linear motion drive shaft along its longitudinal axis is less than 3mm, more preferably 2mm, under the influence of said reciprocating linear motion drive force.
In yet another embodiment, the powered cleaning and care implement is a powered toothbrush having a drive shaft with reciprocating rotational motion about a longitudinal axis thereof, and the support structure is a rotational motion support structure for supporting the reciprocating rotational motion of the drive shaft. Under the action of the driving force of the reciprocating rotation, the inner end of the rotating motion supporting structure elastic element makes reciprocating bending motion around the outer end of the rotating motion supporting structure elastic element. Preferably, the maximum angle of rotation of the reciprocating rotary motion drive shaft about its longitudinal axis is less than 40 degrees in magnitude, more preferably 25 degrees in magnitude.
In the invention, because the numerical ratio between the thickness of the cross section perpendicular to the radial direction of the driving shaft of the supporting structure elastic part along the direction parallel to the driving force and the width of the cross section perpendicular to the driving force is reasonably selected, for the driving shaft doing reciprocating linear motion, the supporting structure elastic part is easy to generate bending deformation in response to the reciprocating linear motion of the driving shaft along the longitudinal axis of the driving shaft under the driving of the reciprocating linear motion driving force, and can also prevent the driving shaft from rotating around the longitudinal axis of the driving shaft, thereby reliably responding to the driving force of the driving shaft to generate elastic bending deformation; in the case of a drive shaft which performs reciprocating rotational motion, the support structure elastic member is not only easy to generate bending deformation in response to the reciprocating rotational motion of the drive shaft about the longitudinal axis thereof, but also can block the motion of the drive shaft along the longitudinal axis thereof, and can reliably generate elastic bending deformation in response to the drive force of the drive shaft. Meanwhile, because the driving shaft is in gapless connection with the supporting structure, the impact and collision to the supporting structure caused by the reciprocating motion of the driving shaft are avoided, and the noise is greatly reduced.
Drawings
FIG. 1 is a front elevational view of a reciprocating linear motion assembly of a reciprocating linear motion drive shaft and its support structure of the present invention, the support structure shown therein including a plurality of support structure springs;
FIG. 2 is a front view of the reciprocating linear motion assembly of FIG. 1 in different operating states, wherein FIG. 2-1 shows the reciprocating linear motion drive shaft in its origin position (i.e., middle position) of its linear motion trajectory, wherein a portion of the reciprocating linear motion support structure mount is visible, FIG. 2-2 shows the reciprocating linear motion drive shaft in its origin position of its linear motion trajectory, wherein the reciprocating linear motion support structure mount is fully disassembled, FIG. 2-3 shows the reciprocating linear motion drive shaft moving upward along its longitudinal axis away from the origin position of the motion trajectory shown in FIG. 2-2, FIG. 2-4 shows the reciprocating linear motion drive shaft moving downward along its longitudinal axis away from the origin position of the motion trajectory shown in FIG. 2-2, FIGS. 2-5 illustrate the linear support structure with the single spring, the reciprocating linear motion drive shaft shown in its origin position in its linear motion path;
FIGS. 3-3 are sectional views of the reciprocating linear motion assembly shown in FIGS. 2-4 in respective operating states, wherein FIG. 3-1 corresponds to the operating state shown in FIG. 2-2, FIG. 3-2 corresponds to the operating state shown in FIG. 2-3, and FIG. 3-3 corresponds to the operating state shown in FIG. 2-4;
FIG. 4 is a front elevational view of the reciprocating rotary motion assembly of the reciprocating rotary drive shaft and its support structure of the present invention, the support structure shown therein including a plurality of support structure springs;
FIG. 5 is a front view of the reciprocating rotary motion combinations of FIG. 4 in different operating states, wherein FIG. 5-1 shows the reciprocating rotary motion drive shaft with the reciprocating rotary motion support structure mount mounted thereon in a position at the origin of its rotary motion profile, FIG. 5-2 shows the reciprocating rotary motion drive shaft in a position at the origin of its rotary motion profile, wherein the reciprocating rotary motion support structure mount is fully disassembled, FIG. 5-3 shows the reciprocating rotary motion drive shaft rotated in a clockwise direction from the position at the origin of the rotary motion profile of FIG. 5-2, and FIG. 5-4 shows the reciprocating rotary motion drive shaft rotated in a counterclockwise direction from the position at the origin of the rotary motion profile of FIG. 5-2;
FIG. 6 is a bottom view of the reciprocating rotary motion assembly shown in FIG. 5 in an operational configuration corresponding to that shown in FIG. 5, wherein FIG. 6-1 corresponds to that shown in FIG. 5-1, FIG. 6-2 corresponds to that shown in FIG. 5-2, FIG. 6-3 corresponds to that shown in FIG. 5-3, and FIG. 6-4 corresponds to that shown in FIG. 5-4;
FIGS. 7-4 are perspective views of the reciprocating rotary motion assembly shown in FIGS. 5-4 in respective operating states, wherein FIG. 7-1 corresponds to the operating state shown in FIG. 5-1, FIG. 7-2 corresponds to the operating state shown in FIG. 5-2, FIG. 7-3 corresponds to the operating state shown in FIG. 5-3, FIG. 7-4 corresponds to the operating state shown in FIG. 5-4, and FIG. 7-5 shows a condition where the rotary support structure includes a single resilient member, the reciprocating rotary motion drive shaft shown in the figures being at the origin of its rotary motion profile;
FIG. 8 is a schematic view of an electric toothbrush incorporating the linear motion assembly shown in FIG. 1;
FIG. 9 is a schematic view of a powered toothbrush incorporating the combination of rotational movements shown in FIG. 4;
figure 10 is a schematic view of a dental irrigator equipped with the linear motion combination shown in figure 1.
Description of the main reference numerals
20 is a linear motion support structure, hereinafter referred to as a straight-branch structure, supporting the reciprocating linear motion drive shaft;
21 is the outer fixed ring of the reciprocating linear motion supporting structure, which is hereinafter referred to as the straight-branch structure outer fixed ring;
22 is an elastic member of the reciprocating linear motion supporting structure, hereinafter referred to as a straight-branch structure elastic member;
23 is an inner fixed ring of the reciprocating linear motion supporting structure, which is hereinafter referred to as a straight-branch structure inner fixed ring;
30, the reciprocating linear motion support structure fixing member, hereinafter referred to as a straight-branch structure fixing member;
40 is a drive shaft that performs reciprocating rotational motion about a drive shaft longitudinal axis, hereinafter referred to simply as a rotating shaft;
50 is a rotary motion support structure, hereinafter referred to as a swivel-support structure, which supports the reciprocating rotary motion drive shaft;
51 is the outer fixed ring of the reciprocating rotary motion supporting structure, which is hereinafter referred to as a rotary-support structure outer fixed ring;
52 is the elastic member of the reciprocating rotary motion supporting structure, hereinafter referred to as a rotary-branched structure elastic member;
53 is the inner fixed ring of the reciprocating rotary motion supporting structure, hereinafter referred to as the rotary-support structure inner fixed ring;
60 is the reciprocating rotary motion support structure mount, hereinafter referred to as a swivel-mount structure mount;
L1a longitudinal axis of the reciprocating linear motion drive shaft;
h1the length of the straight-branch structure elastic element along the radial direction of the reciprocating linear motion driving shaft;
b1for the straight-branched structure elastic member to extend perpendicularly to the driving force F in a cross section perpendicular to the radial direction of the driving shaft1The width of the direction;
t1for the straight-branched structure elastic member to extend in parallel to the driving force F in a cross section perpendicular to the radial direction of the driving shaft1A thickness in a direction;
L2a longitudinal axis of the reciprocating rotary motion drive shaft;
h2the length of the rotary-support structure elastic element along the radial direction of the reciprocating rotary motion driving shaft;
b2for the elastic member of the screw-support structure to extend perpendicularly to the driving force F in a cross section perpendicular to the radial direction of the driving shaft2The width of the direction;
t2for the elastic member of the screw-support structure to be parallel to the driving force F in a cross section perpendicular to the radial direction of the driving shaft2A thickness in a direction;
F1a force for driving said drive shaft in a reciprocating linear motion along a longitudinal axis thereof;
F2a force for driving the drive shaft in a reciprocating rotational movement about its longitudinal axis.
Detailed Description
In the description below of the present application, terms expressing relative spatial positions, such as "inner," outer, "" upper, "" lower, "" upper (or upper end), "lower (or lower end)," and the like, are used to describe simply the relationship of one element or feature to another element(s) or feature(s) as shown in the figures. In this specification, "inner" and "outer" are relative to the radial direction of the electric cleaning and care implement, with inner being defined adjacent to the center thereof and outer being defined away from the center; "upper", "lower", and "lower" are relative to the longitudinal axis of the electric toothbrush, and the end adjacent to the bristle is defined as "upper", or "upper", and the end opposite thereto is defined as "lower", or "lower", when the electric cleaning and care implement is in the upright or inclined operating state.
When an element is described as being "at … …" or "coupled" to another element, it can be directly at or coupled to the other element or intervening elements may be present. And when an element is referred to as being "directly on … …" or "directly coupled" to another element, there are no elements present therebetween. Other words describing the relationship between elements should be understood to have similar meanings (e.g., "between … …" as opposed to "directly between … …", etc.).
The stationary device housing (not shown) of the present invention comprises an upper housing and a lower housing, the lower housing comprising at least a portion of the drive shaft 10 or 40 and a support structure 20 or 50 for supporting the drive shaft 10 or 40, at a driving force F1Or F2By driving the shaft 10 or 40 along its longitudinal axis L1Or about its longitudinal axis L2And the lower shell of the device can do reciprocating linear motion or reciprocating rotary motion relative to the lower shell of the device. The device comprises, in the upper housing, a head driven by a drive shaft 10, 40, the transverse axis L of which3、L4Substantially perpendicular to the longitudinal axis L of the drive shaft 10, 401、L2. Fig. 1-3 show the drive shaft 10 along its longitudinal axis L1In the case of a reciprocating linear movement, fig. 4-7 show the drive shaft 40 about its longitudinal axis L2And reciprocating and rotating.
Referring to fig. 1-7, the support structure 20, 50 of the present invention comprises a support structure inner retainer ring 23, 53, at least one support structure elastic member 22, 52 and a support structure outer retainer ring 21, 51, wherein fig. 2-5 and 7-5 illustrate a case where the support structure elastic member is one, and fig. 2-1 to 2-4 and 7-1 to 7-4 illustrate a case where the support structure elastic member is plural. The support structure outer retainer ring 21, 51, the support structure spring 22, 52 and the support structure inner retainer ring 23, 53 may be made of plastic, preferably thermoplastic. The support structure inner retainer ring 23, 53 is secured to the drive shaft 10, 40 in the circumferential direction of the drive shaft, and the support structure inner retainer ring 23, 53 moves with the reciprocating drive shaft 10, 40 without relative movement therebetween. The retaining ring 23, 53 and the drive shaft 10, 40 in the support structure may be injection molded together as a single piece or may be separate pieces fastened together by fittings. The outer retaining ring 21, 51 of the support structure is fastened to the inner wall of the lower housing of the device directly or via the support structure fastening means 30, 60 in the circumferential direction of the lower housing of the device, without relative movement between the outer retaining ring 21, 51 of the support structure and the support structure fastening means 30, 60 (when fastened via the fastening means) and the lower housing of the device, i.e. the outer retaining ring 21, 51 of the support structure is stationary relative to the lower housing of the device, 30, 60. At least one support structure elastic member 22, 52 is disposed between the support structure outer fixing ring 21, 51 and the support structure inner fixing ring 23, 53, but the present invention is not limited thereto, and the support structure elastic member 22, 52 of the present invention may be integrally coupled with the support structure 20, 50 inner and outer fixing rings 21, 51 and 23, 53, for example, in a circular ring shape, or may be a portion of the support structure elastic member coupled with a portion of the inner and outer fixing rings. None of these modifications depart from the scope of the present invention. Furthermore, the cross-section of the support structure spring 22, 52 perpendicular to the radial direction of the drive shaft may be any shape, such as a polygon or a combination of straight and curved segments, without departing from the scope of the present invention.
As shown in fig. 2-5 and 6-2-6-4 and 7-5, one end of the support structure springs 22, 52 fixed to the support structure outer retainer rings 21, 51 is an outer end A, C, and the other end of the support structure springs 22, 52 fixed to the support structure inner retainer rings 23, 53 opposite the outer end A, C is an inner end B, D. Of course, the lower housing or the reciprocating driving shaft of the device can also be in other shapes, and the inner and outer fixing rings of the supporting structure can also be in shapes matched with the lower housing or the reciprocating driving shaft of the device.
Fig. 1 to 3 show the driving shaft 10 in a reciprocating linear motion. Referring to fig. 2-2, 2-5 and 3-1, when the translation shaft 10 is at the origin position of its reciprocating linear motion trajectory (the middle position of the linear reciprocating motion trajectory), the straight-branch structure 20 is also at the origin position, and at this time, the straight-branch structure elastic member 22 is in a free state, and the straight-branch structure elastic member 22 is not elastically deformed by bending. Referring to fig. 2-3 and 3-2, the translation shaft 10 is displaced from the origin along its longitudinal axis L1When moving upwards, as the straight-supporting structure inner fixed ring 23 and the translational shaft 10 are fastened, the translational shaft 10 drives the straight-supporting structure inner fixed ring 23 to move upwards, the straight-supporting structure inner fixed ring 23 drives the inner end B of the straight-supporting structure elastic part 22 to move upwards along with the straight-supporting structure inner fixed ring, the outer end A of the straight-supporting structure elastic part is fixedly connected with the straight-supporting structure outer fixed ring 21, and the straight-supporting structure outer fixed ring 21 is static relative to the lower device shell, so that the translational shaft 10 generates relative movement relative to the straight-supporting structure elastic part outer end A. The straight-branched structure elastic member 22 is elastically deformed in bending by the relative movement of the translation shaft 10. More specifically, when the translational shaft 10 drives the inner end B of the straight-branched structure elastic member 22 to move upward away from the original position, the inner end B of the straight-branched structure elastic member 22 generates an upward bending movement with respect to the outer end a of the straight-branched structure elastic member 22, and the straight-branched structure elastic member 22 generates an upward bending deformation. The displacement of the current position of the inner end B of the straight-branched structural elastic member 22 relative to the position of the inner end B of the elastic member 22 in the free state is the upward deflection of the straight-branched structural elastic member 22. FIGS. 2-4 and 3-3 show the translational axis 10 displaced from the origin position along its longitudinal axis L1A downward motion condition. Because the inner fixed ring 23 of the straight-supporting structure and the translational shaft 10 are fastened, when the translational shaft 10 moves downwards away from the original point position, the inner fixed ring 23 of the straight-supporting structure is driven to move downwards, and the inner end B of the elastic part 22 of the straight-supporting structure is driven to move downwardsAnd (6) moving. Since the outer end a of the straight-supporting structure elastic member 22 is tightly coupled to the straight-supporting structure outer retainer ring 21 and the straight-supporting structure outer retainer ring 21 is stationary with respect to the apparatus lower case, the outer end a of the straight-supporting structure elastic member 22 is stationary with respect to the apparatus lower case, the translational shaft 10 is relatively moved with respect to the outer end a of the straight-supporting structure elastic member 22, and the straight-supporting structure elastic member 22 is elastically deformed by the relative movement of the translational shaft 10. More specifically, when the translational shaft 10 moves the inner end B of the straight-branched structure elastic member 22 downward away from the free state of the elastic member, the inner end B of the straight-branched structure elastic member 22 makes a downward bending motion with respect to the outer end a thereof, and the straight-branched structure elastic member 22 makes a downward bending deformation in a direction opposite to the direction of the bending deformation made when the translational shaft 10 moves upward away from the origin position. The displacement of the current position of the inner end B of the straight-branched structural elastic member 22 relative to the position of the inner end B of the elastic member 22 in the free state is the downward deflection of the straight-branched structural elastic member 22. Accordingly, when the driving shaft 10 makes a reciprocating linear motion, the inner end B of the straight-branch structure elastic member 22 is driven to make an upward-downward reciprocating bending motion around the outer end a of the elastic member, and the straight-branch structure elastic member 22 makes an upward-downward bending deformation.
As described above, the translation shaft 10 linearly reciprocates relatively to the outer stationary ring 21 of the straight-branched structure. The outer and inner ends, i.e., A, B ends, of the straight-branched structure elastic member 22 are respectively and fixedly coupled to the straight-branched structure outer fixing ring 21 and the straight-branched structure inner fixing ring 23, and the straight-branched structure elastic member 22 has a spring property, which is equivalent to a bending elastic member. The straight-support structure inner fixed ring 23 and the straight-support structure elastic piece 22 are tightly connected with the moving shaft 10 without gaps, namely the moving shaft 10 and the B end of the straight-support structure elastic piece 22 are tightly connected with each other without gaps, and the straight-support structure inner fixed ring 23, the B end of the straight-support structure elastic piece 22 and the moving shaft 10 have the same linear velocity, so that the fixed connection without gaps can ensure that the moving noise between the moving shaft 10 and the straight-support structure 20 is small.
The straight-branched structure elastic member 22 is set to be perpendicular to the driving force F in a cross section perpendicular to the radial direction of the driving shaft1Has a dimension of width b1(ii) a The straight-branch structure elastic member22 in a cross section perpendicular to the radial direction of said drive shaft, along a plane parallel to the driving force F1Is the thickness t1In one embodiment of the present invention, b is selected1Greater than t1Triple of, i.e. b1＞3t1. When the straight-branch structure elastic member 22 is subjected to a force from a direction tangential to the circumferential direction of the translation shaft 10, the bending deformation section coefficient of the straight-branch structure elastic member 22 corresponding to the generated bending deformation is set to be the circumferential bending deformation section coefficient Iz1The straight-supported structure elastic member 22 is subjected to a longitudinal axis L parallel to the translation shaft 101Directional force (i.e., driving force F)1) The bending deformation section coefficient of the straight-branch structure elastic member 22 corresponding to the generated bending deformation is the axial bending deformation section coefficient Iz2Coefficient of section of axial bending deformation Iz2It is also understood that the straight-branched structure elastic member 22 is formed along the longitudinal axis L of the translation shaft 10 in a cross section perpendicular to the radial direction of the drive shaft1Direction (driving force F)1Direction (d) of the thickness t1When bending deformation is generated in the stress direction, the transverse section of the transverse shaft is along the longitudinal axis L of the translation shaft 101Thickness t in the direction1And its circumferential direction along the translation axis 10 (perpendicular to the driving force F) in said cross section1Direction (d) of the width (b)1The coefficient of the bending deformation section of the formed cross section. Because b is reasonably selected in the embodiment1And t1Numerical ratio of (1), axial bending deformation section coefficient I of the straight-branched structure elastic member 22z2Can be far less than the circumferential bending deformation section coefficient Iz1Axial bending deformation section coefficient Iz2Even less than the circumferential bending deformation section coefficient Iz1One ninth of (I)z2＜Iz1/9), therefore, the straight-branched structural elastic member 22 is not only easily responsive to the translational shaft 10 along the drive shaft longitudinal axis L1Reciprocating to generate bending deformation and can also block the translational shaft 10 from rotating around the longitudinal axis L thereof1The linear-branch structure elastic piece 22 can reliably respond to the driving force F of the translational shaft 10 under the driving of the reciprocating linear motion of the driving shaft 10 by rotating1And a corresponding elastic bending deformation occurs. In the inventionThe bending deformation section is a straight-branch structure elastic part 22 composed of t1And b1The cross section of the structure. Obviously, in the circumferential direction (perpendicular to the driving force F) along the translation axis 101Direction of) the straight-branched structure elastic member 22 is harder to bend.
In the present invention, the straight-branch structure inner fixed ring 23 and the translational shaft 10 are fixedly connected, the maximum amplitude of the translational shaft 10 is approximately equal to the maximum deflection of the straight-branch structure elastic member 22, and the maximum amplitude of the translational shaft 10 refers to the maximum displacement of the translational shaft 10 from the origin of the trajectory corresponding to the free state of the straight-branch structure elastic member 22 to the upper (or lower) side.
In addition, because the straight-supporting structure inner fixed ring 23 is fixedly connected with the translational shaft 10, the straight-supporting structure inner fixed ring 23 is along the longitudinal axis L of the translational shaft 101The thickness of the direction is larger than that of the straight-supporting structure elastic part 22 along the longitudinal axis L of the translation shaft 10 on the cross section perpendicular to the radial direction of the driving shaft1Direction (i.e. driving force F)1Direction) of the thickness t1Thereby, it is possible to ensure that the straight-supported structure inner retainer ring 23 and the flat moving shaft 10 are firmly coupled.
In the present invention, as shown in fig. 3-1, the distance between the upper surface of the inner and outer fixing rings 21, 23 of the straight-supporting structure 20 and the head may be designed to be smaller than the distance between the upper edge of the straight-supporting structure elastic member 22 and the head, or the distance between the lower surface of the inner and outer fixing rings 21, 23 of the straight-supporting structure 20 and the head may be designed to be larger than the distance between the lower edge of the straight-supporting structure elastic member 22 and the head, so that the combined straight-supporting structure 20 extends along the longitudinal axis L parallel to the translation shaft 101At least one of the upper side or the lower side of the cross section of (a) is concave, that is, at least one of the upper side or the lower side of the cross section of the combined straight-supporting structure 20 along the direction parallel to the motion direction of the translation shaft 10 is concave.
As described above, the straight-branched structure elastic member 22 has a spring characteristic, and according to the spring oscillator principle, the driving kinetic energy of the translational shaft 10 can be converted into the elastic potential energy of the straight-branched structure elastic member 22, and likewise, the elastic potential energy of the straight-branched structure elastic member 22 can be converted into the driving kinetic energy of the translational shaft 10. Elastic potential energy of the straight-support structure elastic member 22 and driving motion of the translation shaft 10Can be repeatedly switched, and the energy loss is very small during switching. When the natural frequency of the elastic system constituted by the straight-branched structure elastic member 22 and the moving frequency of the translational shaft 10 are in the resonance range, i.e., the ratio of the natural frequency of the elastic system to the moving frequency of the translational shaft 10 is 75% to 125%, the conversion of the elastic potential energy and the driving kinetic energy between the straight-branched structure elastic member 22 and the translational shaft 10 hardly generates energy loss. For this purpose, the straight-branched structure elastic member 22 may be designed such that a cross section perpendicular to the radial direction of the translation axis 10 is rectangular, and in this case, the straight-branched structure elastic member 22 has an equivalent spring stiffness coefficient K1r＝n*E*b1r*t1r 3/(4*h1r 3) Where n is the equivalent number of straight-branched structure elastic members 22; e is the elastic modulus of the material; b1r、t1r、h1rB of the straight-branched structural elastic member 22 corresponding thereto when the cross section of the straight-branched structural elastic member 22 is rectangular1、t1、h1. As can be seen from the principle of the elastic vibrator,
m1ris the mass of the elastic system. Rational selection of b1r、t1r、h1rThe value of (A) or the numerical ratio therebetween, a desired equivalent spring stiffness coefficient K can be obtained1rSo that the natural frequency of the elastic system constituted by the straight-branched structure elastic member 22 can be obtained as desired, and thus, when the natural frequency of the elastic system constituted by the straight-branched structure elastic member 22 and the frequency of the linear motion of the translational shaft 10 are in the resonance range, there is almost no energy loss between the straight-branched structure elastic member 22 and the translational shaft 10. The straight-branched structure elastic member 22 may be designed such that a cross section perpendicular to the radial direction of the translation axis 10 is triangular, and in this case, the straight-branched structure elastic member 22 has an equivalent spring stiffness coefficient K1s＝n*E*b1s*t1s 3/(12*h1s 3) Where n is the equivalent number of straight-branched structure elastic members 22; e is the elastic modulus of the material;b1s、t1s、h1sb of the straight-branched structural elastic member 22 respectively corresponding to the straight-branched structural elastic members 22 when the cross section of the straight-branched structural elastic member 22 is triangular1、t1、h1. As can be seen from the principle of the elastic vibrator,
m1sis the mass of the elastic system. Likewise, reasonably select b1s、t1s、h1sThe value of (A) or the numerical ratio therebetween, a desired equivalent spring stiffness coefficient K can be obtained1rSo that the natural frequency of the elastic system constituted by the straight-branched structure elastic member 22 can be obtained as desired, and thus there is almost no energy loss between the straight-branched structure elastic member 22 and the translational axis 10 when the natural frequency of the elastic system constituted by the straight-branched structure elastic member 22 and the translational axis linear motion frequency are in the resonance range. In addition, the natural frequency of the elastic system formed by the straight-branched structure elastic member 22 can also be obtained through experiments.
Fig. 4-7 show the drive shaft 40 about its longitudinal axis L2Relative to the situation that the lower shell of the device does reciprocating rotation motion. In this embodiment, at least a portion of the rotatable shaft 40 is mounted in the lower housing of the device and a rotational movement support structure 50 for supporting the rotatable shaft 40, the remainder of the rotatable shaft 40 being extendable into the upper housing of the device, and a head portion driven by the rotatable shaft 40 is mounted in the upper housing of the device, the transverse axis of the head portion being substantially perpendicular to the longitudinal axis L of the rotatable shaft 402. The swivel-support structure 50 includes a swivel-support structure outer retainer ring 51, at least one swivel-support structure elastic member 52, and a swivel-support structure inner retainer ring 53. The swivel-support structure is such that the stationary ring 53 is secured to the swivel shaft 40 without relative movement therebetween. The spin-support structure inner retainer ring 53 rotates as the rotation shaft 40 rotates. The swivel-support structure outer retainer ring 51 is fastened to the inside of the lower case of the device directly or by the swivel-support structure retainer 60, and the swivel-support structure outer retainer ring 51 is fastened with respect to the swivel-support structure retainer 60 (when fastened by the retainer)) And the device lower housing is stationary. At least one screw-support structure elastic member 52 is disposed between the screw-support structure outer fixing ring 51 and the screw-support structure inner fixing ring 53, as shown in fig. 6-2 to 6-4 and 7-5, an outer end C of the screw-support structure elastic member 52 is fixedly coupled to the screw-support structure outer fixing ring 51, and an inner end D of the screw-support structure elastic member 52 is fixedly coupled to the screw-support structure inner fixing ring 53. Fig. 6-2, 7-2 and 7-5 show the case where the swivel-support structure 50 is at the origin of the reciprocating rotational motion locus of the rotational shaft 40, when the rotational shaft 40 is around its longitudinal axis L2The deflection angle of the rotation is zero, the spiral-branched structure elastic member 52 is in a free state, and the elastic member 52 is not elastically deformed by bending. Referring to fig. 6-3 and 7-3, when the rotary shaft 40 moves in a clockwise direction from the origin position of its reciprocating rotational motion trajectory, since the rotation-support structure inner fixed ring 53 is fastened to the rotation shaft 40, the inner end D of the rotation-support structure elastic member 52 is fastened to the rotation-support structure inner fixed ring 53, the rotation shaft 40 drives the rotation-support structure inner fixed ring 53 to rotate in the clockwise direction, the rotation-support structure inner fixed ring 53 drives the inner end D of the rotation-support structure elastic member 52 to rotate in the clockwise direction, and the outer end C of the swivel-support structure elastic member 52 is tightly coupled to the swivel-support structure outer fixing ring 51, the outer ends C of the swivel-support structure outer fixing ring 51 and the swivel-support structure elastic member 52 are stationary with respect to the apparatus lower case, and the rotational shaft 40 moves with respect to the swivel-support structure outer fixing ring 51 and the outer end C of the swivel-support structure elastic member 52. The inner end D of the swing-support structure elastic member 52 is stationary with respect to the rotation shaft 40, and the swing-support structure elastic member 52 is elastically bent and deformed by the rotation shaft 40. More specifically, when the rotating shaft 40 moves the inner end D of the screw-support structure elastic member 52 in the clockwise direction away from the free state of the elastic member 52, the screw-support structure elastic member 52 is bent and deformed in the counterclockwise direction about the outer end C thereof. The displacement of the position of the inner end D of the current pivot-support structure elastic member 52 relative to the position of the inner end D of the elastic member in the free state is the counterclockwise deflection of the elastic member 52. Referring to fig. 6-4 and 7-4, they show the case where the rotation axis 40 moves in the counterclockwise direction from the origin position of the reciprocating rotational motion trajectory. Since the inner stationary ring 53 of the swivel-support structure is fastened to the rotary drive shaft 40,the rotary driving shaft 40 drives the rotation-support structure inner fixed ring 53 to move counterclockwise, the inner end D of the rotation-support structure elastic member 52 is fixedly coupled to the rotation-support structure inner fixed ring 53, the inner end D of the rotation-support structure elastic member 52 is also driven to move counterclockwise, the outer end C of the rotation-support structure elastic member 52 is fixedly coupled to the rotation-support structure outer fixed ring 51, the rotation-support structure outer fixed ring 51 is stationary with respect to the apparatus lower case, the rotating shaft 40 rotates with respect to the rotation-support structure outer fixed ring 51, the inner end D of the rotation-support structure elastic member 52 rotates with respect to the outer end C of the rotation-support structure elastic member 52, the rotation-support structure elastic member 52 is elastically deformed by the rotating shaft 40, more specifically, when the rotating shaft 40 drives the inner end D of the rotation-support structure elastic member 52 to move counterclockwise from the free state of the elastic member 52, the inner end D of the swivel-support structure elastic member 52 is rotated in a clockwise direction about the outer end C thereof. The displacement of the position of the inner end D of the elastic member 52 of the current pivot-support structure relative to the position of the inner end D of the elastic member 52 in the free state is the clockwise deflection of the elastic member 52.
Referring to fig. 4-7, the rotation shaft 40 drives the rotation-support structure elastic member 52 to perform a reciprocating, clockwise-counterclockwise bending motion around the outer end C of the elastic member 52, and the rotation-support structure elastic member 52 corresponds to an elastic member. The rotation-support inner fixed ring 53 is fastened to the rotation shaft 40, and the rotation-support inner fixed ring 53 and the rotation shaft 40 have the same angular velocity. The rotary shaft 40 and the fixing ring 53 in the screw-support structure are tightly coupled without a gap, and the rotary shaft 40 is equivalently coupled to the elastic member 52 of the screw-support structure without a gap. The dimension of the spiral-branched elastic member 52 in the radial direction of the rotational shaft 40 is set to a length h2The rotation-support structure elastic member 52 is formed perpendicularly to the driving force F in a cross section perpendicular to the radial direction of the driving shaft2The dimension in the direction is width b2The rotation-support structure elastic member 52 is arranged in parallel to the driving force F in a cross section perpendicular to the radial direction of the driving shaft2The dimension in the direction is the thickness t2Preferably b2＞3t2. When the spiral-branch structure elastic member 52 is subjected to bending deformation caused by a force in the circumferential tangential direction from the rotating shaft 40, the bending deformation section coefficient corresponding to the spiral-branch structure elastic member 52 is set to be circumferential bending deformationSection modulus Iz3The coefficient of section I of the circumferential bending deformation can also be setz3It is understood that the spiral-branched structure elastic member 52 is formed by b when it receives a force in a direction tangential to the circumference of the rotary shaft 402And t2Coefficient of circumferential bending deformation section of composed cross section Iz3The rotation-support structure elastic member 52 is set to be parallel to the longitudinal axis L of the rotation shaft 402When a force is applied in a certain direction, the bending deformation section coefficient of the rotary-support structure elastic member 52 corresponding to the generated bending deformation is the axial bending deformation section coefficient Iz4Coefficient of axial bending deformation cross section Iz4It is also understood that the swivel-support structure 52 is subject to a longitudinal axis L parallel to the axis of rotation 402In the direction of force, from b2And t2Coefficient of axial bending deformation of cross section of composition Iz4. Because b is reasonably selected in the invention2And t2A numerical ratio of (a) such that b2>3t2And thus the axial bending deformation section coefficient I of the spiral-branched structure elastic member 52z4Far greater than the circumferential bending deformation section coefficient Iz3Coefficient of circumferential bending deformation section Iz3Even less than the axial bending deformation section coefficient Iz4One ninth of (I)z3＜Iz4/9), therefore, the rotation-support structure elastic member 52 can reliably generate elastic bending deformation in response to the driving force of the rotating shaft 40, driven by the reciprocating rotational motion of the driving shaft 40. In the present invention, the bending deformation section is a part b of the spiral-branch structure elastic member 522And t2Cross-section of the composition. It is apparent that the rotation-branch structure elastic member 52 is easily bent by a force along the circumferential direction of the rotation shaft 40, and thus the rotation-branch structure elastic member 52 can be elastically bent and deformed in reliable response to the driving force of the rotation shaft 40 by the reciprocating rotational motion of the driving shaft 40.
In this embodiment, the rotation-branch structure inner fixed ring 53 is fixedly connected to the rotation driving shaft 40, and the maximum clockwise (or counterclockwise) rotation angle reached by the rotation driving shaft 50 away from the locus point corresponding to the free state of the elastic member 52 is substantially equal to the maximum counterclockwise (or clockwise) rotation angle of the rotation-branch structure elastic member 52.
Other exemplary embodiments of the present invention are further described below in conjunction with figures 8-10, taking as an example an electric toothbrush and a dental irrigator. Although the following description will be made by taking an electric toothbrush and a tooth irrigator as examples, the present invention is not limited thereto, and the present invention is also applicable to other electric cleaning and nursing appliances having a reciprocating drive shaft, such as a face washer, a shaver, and the like.
Fig. 8 is a schematic view of an electric toothbrush equipped with the combination of reciprocating linear motion shown in fig. 1, fig. 9 is a schematic view of an electric toothbrush equipped with the combination of reciprocating rotational motion shown in fig. 4, and fig. 10 is a schematic view of a tooth irrigator equipped with the combination of reciprocating linear motion shown in fig. 1.
As shown in fig. 8, a driving shaft (translational shaft) 10 of the electric toothbrush, which makes a reciprocating linear motion, is arranged in a lower housing S-1 of the handle and extends into an upper housing S-2 of the handle, a brush head driven by the translational shaft 10 is also arranged in the upper housing S-2 of the handle, bristles S-3 for cleaning teeth are distributed on the brush head, and an axis L of the bristles S-33Substantially perpendicular to the longitudinal axis L of the translation shaft 101. In the embodiment shown in fig. 10, the translational shaft 10 is arranged in the lower shell C-1 of the tooth irrigator, and the flushing head is arranged in the shell C-2 of the flushing head, and the flushing liquid driven by the translational shaft 10 flows out through the flushing head. For such an electric cleaning and nursing tool, the maximum amplitude of the translational axis 10 is small, about 2mm, and therefore, the straight-supporting structure 20 of the present invention is particularly suitable for the electric cleaning and nursing tool having the maximum amplitude of the translational axis 10 smaller than 3 mm. More specifically, the straight-supporting structure 20 of the present invention is suitable for use in an electric cleaning and nursing product having a total displacement of the translational axis 10 from top to bottom of less than 6 mm. For durability, it is generally desirable that the drive shaft of the motorized cleaning and care implement withstand more than 10 ten thousand reciprocations, for which purpose the straight-branched structured elastic member 22 is disposed along a length h in the radial direction of the translation shaft 101Designed to be larger than the straight-branched structure elastic member 22 in a cross section perpendicular to the radial direction of the drive shaft along the longitudinal axis L of the translation shaft 101Direction (i.e. driving force F)1Direction) of the thickness t1Triple of, i.e. h1＞3t1To ensure the life of the straight-supporting structure elastic member 22 in the electric cleaning and nursing toolThe reciprocating bending deformation can be reliably realized. The applicant has further concluded, through numerous tests, that the straight-branched structural elastic elements 22, in a cross section perpendicular to the radial direction of the driving shaft, lie along the longitudinal axis L of the translation shaft 101Direction (driving force F)1Direction) of the dimension t1Preferably in the range of 0.1mm to 1.3mm, more preferably the straight-branched structural elastic elements 22 are along the longitudinal axis L of the translation shaft 10 in a cross section perpendicular to the radial direction of said drive shaft1Direction (driving force F)1Direction) of the thickness t1The value range of (A) is 0.2mm-0.7 mm.
In the embodiment shown in fig. 8, the pressure exerted by the teeth on the bristles S-3 is generally perpendicular to the longitudinal axis L of the translational shaft 101The pressure exerted by the teeth on the bristles S-3 is equivalently applied to the straight-support structure elastic members 22, which is equivalent to the application of force (pressure or tension) in the direction from the inner ends B to the outer ends a of the straight-support structure elastic members 22. According to Newton' S third law, the straight-branched structure elastic member 22 generates a resistance force against the pressure (or tension) applied to the bristle S-3 by the teeth, the resultant direction of the resistance force being substantially perpendicular to the longitudinal axis L of the translation shaft1And in a direction opposite to the pressure applied by the teeth to the bristles S-3. Therefore, the straight-supported structure elastic member 22 restricts the movement of the translational shaft 10 in the radial direction, and the straight-supported structure elastic member 22 restricts the translational shaft 10 in the direction perpendicular to the longitudinal axis L thereof1The straight-branched structure elastic member 22 supports the translation shaft 10 in the radial direction of the translation shaft 10. Because the straight-branch structure elastic part 22 supports the driving shaft 10 along the radial direction of the translation shaft 10, the direction of the supporting force generated by the straight-branch structure elastic part 22 forms 90 degrees with the movement displacement direction of the translation shaft 10, the straight-branch structure inner fixed ring 23 is fixedly connected with the translation shaft 10, and no friction force needs to be overcome between the straight-branch structure inner fixed ring 23 and the translation shaft 10 to do work, no energy loss is generated when the straight-branch structure 20 supports the driving shaft 10 along the radial direction of the translation shaft 10.
In the invention, the straight-support structure 20 can not only restrain the radial motion of the translation shaft 10, but also form effective support for the translation shaft 10, and the translation shaft 10 is coupled with the inner fixed ring 23 of the straight-support structure 20 without a gap, thereby avoiding the impact and collision of the translation shaft 10 on the straight-support structure 20 and greatly reducing the noise. In addition, the energy loss of the reciprocating conversion of the elastic potential energy of the straight-branched structure elastic member 22 and the driving kinetic energy of the translational shaft 10 is small.
Referring to fig. 9, a driving shaft 40 of the electric toothbrush, which performs a reciprocating rotation motion, is provided in a lower handle case S-4 and extends into an upper handle case S-5, a brush head driven by the driving shaft 40 is further installed in the upper handle case S-5, bristles S-6 for cleaning teeth are distributed on the brush head, and an axis L of the bristles S-64Substantially perpendicular to the longitudinal axis L of the rotating shaft 402. For a power-driven cleaning and nursing tool such as a power toothbrush, the rotating shaft 40 has a small rotating angle amplitude of about 25 degrees, and therefore, the rotation-support structure 50 of the present invention is suitable for a power-driven cleaning and nursing tool in which the maximum rotating angle amplitude of the rotating shaft 40 is less than 40 degrees, and more particularly, the rotation-support structure 50 of the present invention is suitable for a power-driven cleaning and nursing tool in which the total rotating angle of the rotating shaft 40 is less than 80 degrees. The total rotation angle of the rotating shaft 40 is twice the magnitude of the maximum rotation angle, and it is also understood that the total rotation angle of the rotating shaft 40 is an angle swept from the leftmost to the rightmost from the center of rotation. For durability, it is generally desirable that the drive shaft of a powered cleaning and care implement be capable of withstanding more than 10 million reciprocating motions. To this end, in a further embodiment of the present invention, the spin-support structure elastic member 52 is disposed such that it has a length h in a radial direction of the rotational shaft 402A driving force F larger than that of the elastic member 52 in a cross section perpendicular to the radial direction of the driving shaft along a direction parallel to the rotation shaft 402Thickness t in the direction2Triple of, i.e. h2＞3t2To ensure the reliable reciprocating bending deformation of the spiral-branch structure elastic member 52 in the life cycle of the electric cleaning and nursing article. The applicant has further found, through extensive experiments, that it is preferable that the thickness t of the spin-support structure elastic member 52 in the circumferential direction of the rotating shaft 40 in a cross section perpendicular to the radial direction of the driving shaft2Is in the range of 0.1mm to 1.3mm, more preferably, t is2The value range of (A) is 0.2mm-0.7 mm.
In contrast to the conventional shaft-hole coupling structure, a reciprocating driving shaft (a reciprocating driving shaft or a reciprocating driving shaft) passes through a shaft sleeve, a movement gap of 0.01mm to 0.03mm generally exists between the shaft sleeve and the reciprocating driving shaft, the shaft sleeve restrains the radial movement of the driving shaft and supports the driving shaft, and irregular radial force is applied to the driving shaft when teeth apply irregular acting force to bristles, and the irregular radial force causes impact and collision between the driving shaft and the shaft sleeve, which can cause large irregular noise. On the other hand, since the sleeve restrains the radial movement of the drive shaft and supports the drive shaft, the drive shaft is in contact with the sleeve when a radial force is applied to the drive shaft, the sleeve supports the drive shaft against the radial force applied to the drive shaft, and friction is generated between the drive shaft and the sleeve, which will hinder the movement of the drive shaft, thereby consuming energy.
In summary, compared with the existing support structure, the support structure for the driving shaft which performs reciprocating rotation motion or reciprocating linear motion provided by the invention has the advantages that on one hand, because the reciprocating driving shaft is in gapless connection with the support structure, the impact and collision of the driving shaft to the support structure caused by reciprocating motion are avoided, and the noise is greatly reduced, and on the other hand, the energy loss of conversion between the elastic potential energy of the elastic part of the support structure and the driving kinetic energy of the driving shaft is very small, so that the structure is simple, the noise is low, and the energy loss is small. In addition, the support structure is preferably made of plastic, is low in cost and is suitable for mass production.
Claims (15)
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010879992.5A CN114099033A (en) | 2020-08-27 | 2020-08-27 | supporting structure |
| JP2023513467A JP7577835B2 (en) | 2020-08-27 | 2021-05-14 | Support structure |
| US18/023,250 US20230310117A1 (en) | 2020-08-27 | 2021-05-14 | Support structure |
| PCT/CN2021/093887 WO2022041853A1 (en) | 2020-08-27 | 2021-05-14 | Support structure |
| EP21859698.9A EP4186468B1 (en) | 2020-08-27 | 2021-05-14 | Support structure for a drive shaft in an electric cleaning care appliance |
| CA3190085A CA3190085A1 (en) | 2020-08-27 | 2021-05-14 | Support structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010879992.5A CN114099033A (en) | 2020-08-27 | 2020-08-27 | supporting structure |
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| Publication Number | Publication Date |
|---|---|
| CN114099033A true CN114099033A (en) | 2022-03-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202010879992.5A Pending CN114099033A (en) | 2020-08-27 | 2020-08-27 | supporting structure |
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| Country | Link |
|---|---|
| US (1) | US20230310117A1 (en) |
| EP (1) | EP4186468B1 (en) |
| JP (1) | JP7577835B2 (en) |
| CN (1) | CN114099033A (en) |
| CA (1) | CA3190085A1 (en) |
| WO (1) | WO2022041853A1 (en) |
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|---|---|---|---|---|
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Also Published As
| Publication number | Publication date |
|---|---|
| JP7577835B2 (en) | 2024-11-05 |
| EP4186468B1 (en) | 2025-03-26 |
| WO2022041853A1 (en) | 2022-03-03 |
| JP2023538696A (en) | 2023-09-08 |
| US20230310117A1 (en) | 2023-10-05 |
| EP4186468A1 (en) | 2023-05-31 |
| EP4186468A4 (en) | 2024-01-03 |
| CA3190085A1 (en) | 2022-03-03 |
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